Triple Offset Butterfly  Valve and Rotary Valves For Sever Services

ABSTRACT

This invention relates to a novel rotary control valve with new joint methods and flow control mechanisms, line-reparability and fully metal seals more particularly to a triple offset butterfly valve or ball valve with those features used for on-off and flow controlling under multiple extreme conditions or in sever service; such as the integrated gasification combined cycle under high temperature and pressure, Fluid Catalytic Cracking under high temperature over 1200 F with hard diamond like catalytic particles, shale fracking process under extreme high pressure and high velocity fluid with solid particles and corrosive additives and other critical applications for products life lasting 5 to 30 years like deepsea flow control systems and nuclear power plants and for the applications of millions cycles like jet or rocket turbine engine fuel delivery systems with high velocity fuel fluid mixed with highly oxidative gas under temperature 1365 F.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of provisional patent applicationSer. No. 61/575,996 filed on Sep. 1, 2011 by Jianchao Shu

FEDERALLY SPONSORED RESEARCH

No

SEQUENCE LISTING OR PROGRAM

No

BACKGROUND

This invention relates to a novel rotary control valve with new jointmethods and flow control mechanisms, line-reparability and fully metalseals more particularly to a triple offset butterfly valve or ball valvewith those novel features used for on-off and flow fluid controllingunder multiple extreme conditions or in sever service; such as therocket engine fuel control system with highly oxidative fluid underextreme temperature of 1350 F, the integrated gasification combinedcycle (IGCC) under high temperature and pressure, Fluid CatalyticCracking Unit (FCCU) under high temperature over 1200 F with harddiamond like catalytic particles, shale fracking process under extremehigh pressure and high velocity fluid with solid particles and corrosiveadditives, other applications with flow fluid with high viscosity infield of chemical plants, or conventional power plants, refiners andoilfield, or other critical applications for products life lasting 5 to30 years like deepsea flow control systems and nuclear power plants andfor the applications of millions cycles like jet or rocket turbineengine fuel delivery systems with high velocity fuel fluid mixed withhighly oxidative gas under temperature 1365 F or higher without failure.

This valve comprises a body with a flow port and a stem bore, a stemkeyed with a disc is disposed in the stem bore to rotate the discbetween open and closed positions, noise/cavitation reducing trims areinstalled in both ends of the flow port to reduce cavitation or noise,this valve is fully sealed in the stem by a simple, reliable metal Kring with laminated metal packings and in the port by full metal waveseat rings instead of conventional laminated seat with metal rings,graphite rings and gasket. It has a simple base structure with versatileconfigurations for various applications and is easy for manufacturingand repair, yet robust and reliable.

Conventional triple offset butterfly valves were developed in 1960, butsince then most features have not been changed, historically there ismisunderstanding that the triple offset mechanism can solve all rotarymetal seal problems, technically it only solve the rubbing problem to asome level, the rubbing happens between the conical seat and conicalseat ring during rotation between 0-90 degrees, it damages the seat andseal ring and cause high torque, leak and seat prematurely to wear outand like the most ball valves, 98% of all existing triple offsetbutterfly valves only solve this rubbing problem between 0-86 degrees atbest, it means that the rubbing still happens between 86 to 90 degrees,only 3 degrees but with 60%-100% contact area, it still causes damage onthe seat, so how to reach 0-89.95 or 0-89.99 degrees of disengagementbecomes an art and a knowhow or trade secret, there are other sevenexisting problems which have nothing to do with triple offset mechanism(1) metal to metal seat seal, there is no good solution so far, eitherthe original solid seat has high leakage under ANSI class III leakage orthe laminated seat with metal rings glued with graphite rings has ANISclass VI leakage at a new condition, but (a) the seat is easily damagedeither by flow or a mating seat ring, it is required that high preloadis to secure a seal between the seat and disc or body with additionalgraphite gasket and constantly replacement for the seat (b) the seat cannot be used on highly oxidative flow applications when temperature isover 850 F (c) high seating torque, on average, operating torque fortriple offset butterfly valves with the laminated seat is at least astwice high as that of the same size of double offset butterfly valve dueto high pre-bolting on the seat as well as the nature of seat structure,moreover the actuation forces are unpredictable at closed position, soit is difficult to automate (2) axial bolting joint between retainingring and seat ring on the disc, most conventional seal ring jointdevices employ direct screws or sleeve to secure seal rings, such amethod not only produces uneven pressing forces on seal rings and seats,but also has a lower reliability with multiple bolting and highprobability of screws falling into a pipe lines under vibration or highcycle conditions, according to Failure Modes and Effects Analysis(FMEA), such a structure has the highest severity in high vibration,high temperature applications like turbine or jet engine systems, a riskof bolts falling in a pipeline system is very high due to vibration,quick cycle and high temperature creep (3) the graphite stem seals, thestem seal with graphite needs excessive packing force and constantreadjustment or replacement of packing, moreover the actuation forcesare unpredictable, so it is difficult to automate, in case of subseaflow devices or nuclear power plants, or jet engine fuel deliverysystem, the constant readjustment is impracticable (4) key/pin jointbetween stem and disc, this conventional joints greatly reduce thestrength of stem with high stress concentration on disc hub and stem aswell as eliminate the freedom for the stem and disc expansion under hightemperature and pressure by a pin joint or have freedom of movement butcause loss motion and backlash with a key joint, as a result, either thejoint method can cause premature damage on seats and seat leak (5) lackof simple mechanism to reduce the cavitation and noise when the valve isused to throttle the flow (6) unidirectional seal and stem galling underhigh thermal cycle or high temperature, although many triple offsetvalve makers claim that their valves are bidirectional, in fact theupstream seal is tended to move the seat away from the body seal ring,moreover there are cumulative clearances between bearing inside diameterand stem, stem and disc hub, body bearing hole and bearing outsidediameter, sometime after sudden closing, the valves start to leak due tothe clearances, so the current solution is to tight the clearances, as aresult, stem will tend to gall with bearing under high temperature orthermal cycle, in short those problems greatly reduce potential usage ofthe triple offset butterfly valve and prevent it from getting moremarket share (7) Inline reparability, in some applications, the valvesare fully welded with the pipe line, so it is impossible for inlinerepair, so replacement for the whole valve or offline repair can costlots money for customers.

In order to overcome the disadvantages or solve the problems of theconventional triple offset butterfly valve, many efforts have been madein the prior arts. The efforts in five fields were made to improve theconventional valves in the prior arts, but those works within a limitedscope.

The first field is for improving the seat seal, many efforts were made,especially in metal to metal seat seal in high temperature, cryogenicenvironments or for highly abrasive or erosive fluid applications. Thesignificant efforts were made by Karl Adam as shown in U.S. Pat. No.3,442,488 (1969), a butterfly valve with a triple offset arrangement forreducing rubbing between a seat and a seal ring or disc and increasingthe life of the seat seal, but the seat seal itself was not improved andhas a solid surface vs. a solid surface seal, such a seal causes highoperation torque, leakage and requires expensive precision machining andassembly. U.S. Pat. No. 4,667,929 to Franco Narduzzi (1986) discloses asimilar offset arrangement on a ball valve, a seat seal is provided witha solid surface on a body against a solid surface on a ball, a seal ringon the ball is made out of a composite metal material with heatresistant and deformable natures, in the reality such an ideal materialis difficult to make, moreover a secure means was not clearly disclosed,the secure means is the other key factor for a good metal seal underhigh temperature, without a good seat secure means, a stable metal seatseal is impossible. U.S. Pat. No. 3,905,577 to Anatole N. Karpenko(1975) discloses a replaceable laminated seat against solid surface ofdisc, this seat would be a good choice for a metal to metal seat seal,but the bolts and rivets are used as a secure means completely constrainthe seat thermal expansion under high temperature, as the temperatureincreases, the seat will deform and loosen a seal. U.S. Pat. No.5,377,954 to Siegbert Adam et al (1995) discloses a metal seat sealwhich has a solid surface vane against a flexible seal ring assembly,the flexible seal ring assembly has multiple rings with one support endand an unmatched seal surface against the vane, such a seat seal isstronger and more stable than seat seal in U.S. Pat. No. 4,037,819, butthe seat seal still is unstable under high pressure or high cyclecondition and also creates a new problem which is fluid seeping betweenthe rings, although edge welded by a laser welder is provided as aremedy, such a weld process brings out another problem which isdeformation of seal ring after welding, such deformation can generatemore leakage on external surfaces of the ring, above all, the seat sealis unstable and vulnerable to fluid contamination and any point damageon the seal. U.S. Pat. No. 5,871,203 to Jerry Gassaway (1999) shows awidely used, laminated seat ring as a replaceable seat ring, but thereplaceable seat ring without a secure means has a disadvantage in hightemperature or high cycle environments, the different thermal expansionbetween a body and the seal ring can cause leakage through the seatring. In short all efforts in the prior arts never address or recognizethe fundamental problems—laminated seat seal mechanism, rigid flat ringdeformation structure with weak graphite rings between them.

The second field is for improving the joint between the seat and theretaining ring. A conventional mechanical joint means for retaining aseat seal assembly on a valve member or body is accomplished by aretaining ring and multiple bolts as shown in U.S. Pat. No. 6,079,695 toJerry Gassaway (2000), such a mechanical joint means requires precisiondrilling and tapping as well as tedious bolting process, any unevenbolting by manual operation or other process can cause a seat leak andheavy seating and unseating torques specially in large size valves or inhigh temperature environments, more importantly this mechanical jointmeans has a high risk of bolts falling into a pipeline system and isprohibited for using in the engines and turbines or other highlyvibrated conditions, so a more reliable retaining device was developedas shown in U.S. Pat. No. 5,692,725 to Hans-Jurgen Fehringer (1997), theretaining device has smaller operating holes which prevents screws orbolts falling into a pipeline system, but the complicated retaining ringcan be used only on a stationary body and not on a movable valve member,such a retaining device does not have a self lock, so any reaction forceby a high vibration or uneven point forces by screws or bolts can causescrews loose and a seat leak. the fundamental disadvantage for axialbolting method is the direction of the seat loading is the same as thatof bolting, so any disengagement between bolt thread and thread holecaused by a creep or vibration will soon amplify, many tests indicateswithout self lock mechanism, such bolting is not safe under highvibrations and temperature conditions.

The third field is for improving the stem seal packing. A packing deviceis one of those efforts shown in U.S. Pat. No. 4,886,241 to James R.Davis et al (1989) and U.S. Pat. No. 4,394,023 to Alberto L. Hinojosa(1983) disclose stem seals with graphite packing for high temperatureapplications, but the stem packing seals require more packing force andconstant readjustment. A survey shows that 50% of the control valvefailures are contributed by excessive stem packing force, the efforts toimprove the stem seal are to add more stem seal packing sets, more sealforce with more storing energy to both rotary and reciprocal stems. Alive load packing device is one of those efforts shown in U.S. Pat. No.5,230,498 to Charles W. Wood (1993), U.S. Pat. No. 5,503,406 to LeonardT. Armstrong (1996) and U.S. Pat. No. 5,860,633 to Ryan E. Murphy et al(1999). Those packing devices are not only expensive, inefficient andunsuitable for temperatures over 460 F, U.S. Pat. No. 6,202,668 toRobert E. Maki (2001) and U.S. Pat. No. 4,082,105 to Hebert Allen (1978)show fire-resistant stem seals. The fire-resistant stem seals areprovided with a first PTFE seal and a secondary metal seal, in case offire or temperature elevation, the secondary metal seal will replace thefirst PTFE seal, but in reality such a stem seal proves to be unreliableand has high leakage. In short, those prior arts in the stem seal fieldhave common disadvantages: Inefficiency of packing loading. According tothe Hook law and Poisson ratio, only about 30% of axial force in mostmaterials is converted to radial displacements of the packing whichhelps fill in the gap between the stem and the packing, in addition offrictions, lower density or material creeps under high temperature, theefficiency of the conversion even becomes worse about 10-20%, so theconventional axial loadings for radial seal packing are inefficient andexpensive to produce. The stem packing is one of those efforts shown inU.S. Pat. No. 4,886,241 to James R. Davis et al (1989) and U.S. Pat. No.4,394,023 to Alberto L. Hinojosa (1983) disclose stem seals withgraphite packing for high temperature applications, but the stem packingseals are subject to more packing force and constant readjustment. Arecent survey shows that 50% of the control valve failures arecontributed by excessive stem packing force. U.S. Pat. No. 7,004,452 toChatufale (2006) shows C ring seal for gate valve, but it isunidirectional and not for high temperature, while U.S. Pat. ApplicationNo. 2011/0084456 A1 reveals a metal C ring with a insert for hightemperature flange seal application, but the C ring only is used forstatic seal in flanges.

The fourth field is for improving the mechanical joint between stem anddisc U.S. Pat. No. 4,483,513 to Anthony C. Summers (1984) and U.S. Pat.No. 4,828,221 to William B. Scobie (1998) disclose improved jointsbetween a stem and a valve member, but the disadvantage is that thejoints eliminate the stem axial freedom, the elimination can forcethermal expansion to damage a seat or cause the stem deformation and aseat leak under high temperature, a conventional solution to the problemis to employ a key joint as shown in U.S. Pat. No. 6,079,695 to JerryGassaway (2000), but the key joint weakens the two hubs where thehighest stress and stress concentration are located and torques areunevenly transferred, moreover the key joint requires an expensivebroaching process for keyway. U.S. Pat. No. 6,029,949 to Robert JosephBrown et al (2000) shows a plate and bolts for securing a stem on avane, the design with the plate and bolts can further weakens the stemand vane and adds the cost for materials as well as machining, and thereis a high risk of the plate and bolts falling into a pipeline systemunder high temperatures or high vibration conditions, such a design isprohibited in the turbine and engine systems, finally US 2008/0203346 A1to Jianchao Shu (2008) shows the two key joints between the stem anddisc, but the design cause high stress concentrations on the stem andmotion loss.

The fifth field is for developing special disc or trim to reduce thenoise and cavitation, for example, in U.S. Pat. No. 6,338,468 to Ogawa,et al. (2002) a enlarged section of valve body was employed to reducecavitation, it is simple and low cost but in small opening, thecavitation still exists, many cases indicates the wall of enlargedsection is first damaged and flow penetrate the wall and cause leak,finally a valve applications is shown in U.S. Pat. No. 4,007,908 toPaul. V Smagghe.

In short, all efforts in the prior arts never address or recognize needsfor replacing the axial retaining ring bolting or the laminated seatwith metal and graphite stem seal and for developing full metal seat andstem seal under high temperature and fundamentally reducing theoperation torque, most efforts are focused on easing the consequencerather than finding the root of cause, finally other inherent problemfor butterfly valve is the upstream load support by the stem rather thanthe stem and seat like ball valve or gate valve, it causesunidirectional seal in most of the butterfly valve if the stem is notproperly constructed.

So the flow control industry has long sought means of improving theperformance of butterfly as well as rotary valve, improving the stemseal, creating a robust bidirectional seat seal, enabling the valve tohandle various flow under multiple extreme conditions.

In conclusion, insofar as I am aware, no such butterfly or such rotaryvalve is formerly developed with fully metal sealed seat, highlyreliable seat retaining device without high preload and risk of boltfalling into a pipeline system, easy manufacturing at low cost they canbe used for controlling bidirectional fluid between full opening andfull closed with no or less cavitation and low noise under multipleextreme conditions or sever service.

SUMMARY

This invention provides a simple, robust, reliable and versatile rotaryvalves; triple offset butterfly valve and ball valve for server serviceor under multiple extreme conditions. This triple offset butterflycomprises a body with a flow port, a reliable, robustwedge-eccentric—thread joint/lock mechanism between a stem and a disc ina middle is provided with two wedge keys and secured by a lock plug forproviding solid joint without reducing of stem strength and loss motion,the stem is disposed by means of spring bearings in the body, springbearings are disposed in the bearing hole in the body to compensatevalve assembly clearances for downstream seal as well as the thermalexpansion of the stem, the full metal wave seats are disposed betweenconical mating solid seat on the body or the disc for providing sealswithout any graphite gasket, the seats are secured by awedge-eccentric-thread join/lock mechanism, which includes retainingring with a wedged groove to receive three wedged lock rings between thedisc and retaining ring, three lock plugs are disposed in the plug holesof the disc, each lock plug has an eccentric groove to hold each lockring as well push the lock bottom up against wedge surfaces of theretaining ring by rotating the plug, in turn, the wedge lock ring isengaged with wedge surface of groove on the retaining ring is providedfor pressing the wave seats, finally a setscrew is disposed in threadhole in the lock plug to prevent the lock plug form rotation. A novelmetal K rings comprise an I ring inserted in a groove of the stem andtwo metal compression rings disposed in the stem below and above the Iring for converting a dynamic radial seal to a dynamic axial seal andproviding spring load on two laminated metal packing below and above Kring under high temperature and high pressure with the leakage between5-50 ppm.

This rotary valve can be constructed with a ball as the closure memberfor the applications which requires either full port or reduced port, apair of right and left segment trims can be used for both ball valve andbutterfly valve disposed between two ends of the flow port on the rotaryvalve body for reducing cavitation or noise, the trim comprises asegment of cylinder bar with multiple holes and a flow port and aninternal surface mated with a disc or ball, such trims provides a veryeffective multiple flow restriction mechanism in a small opening between0-60 degree where most cavitations happen, the trims can be installed onthe body either by means of two position pins to prevent the segmenttrim from rotation and a step on the body edge to secure the segmenttrim in a valve axial direction, or by a pair of eccentric lock ringsdisposed a groove between the body and a groove on the trim, so as thelock rings are rotated into grooves, the thickness of rings due to theeccentric nature is increased until the both side of the ring areengaged with bottoms of the groove and to secure the trim, in case ofhigh velocity applications, a spot welding may need on the tip of lockrings.

This valve body can be constructed for seat replaceable service on thefield, so the seats on those fully weld body valve still can bereplaceable without cutting the pipes or body, such inline replaceablefeature is very useful for both butterfly valve and ball valve in LNGplant and refiner or gas line, the structure comprises a wedge openingon the body to receive a wedge cover with a gasket around the edge, abody gasket is provided as a secondary seal, a body ring with internalconical surface is engaged with body gasket against the substantiallysame conical surface of outside body and the cover, bolts and nuts areprovided for securing the body and the body ring, finally a pair ofwedge rings are installed to adjust axial gaps after a seat is replaced.

Accordingly, besides objects and advantages of the present inventiondescribed in the above patent, several objects and advantages of thepresent invention are:

(a) To provide simple highly sealable, reliable, durable seat sealassembly for multiple extreme conditions: high pressure, cryogenic orhigh temperature or solid particles with corrosive fluid, so such a sealseat assembly can keep good static and dynamic seals with low leakagebetween 5-50 ppm with low friction and operating torque without highpreload and side seal.(b) To provide a highly reliable joint/lock mechanism between seat andretaining ring for a valve, so such a valve can be operated under highvibration and high temperature condition without risk of bolts fallinginto a pipeline system to damage critical equipment in the downstream(c) To provide a stem seal for extreme conditions: high pressure,cryogenic or high temperature or fire-safe applications. Such a sealring can keep good static and dynamic seals with low leakage between5-50 ppm with low friction without constant repacking or readjustment.(d) To provide a reliable stem/disc joint mechanism for a rotary valve,so the joint/lock mechanism can not only increase the disc and stemstrength and eliminate backlash and motion loss and reduce stressconcentration on stem and disc, also it can prevent stem or hub fromcracking or key from falling into pipeline under vibration or quickcycle applications as well as make easy to manufacture and disassemble.(e) To provide a valve with bearings to support a stem under hightemperature, high thermal cycle and high pressure, compensate a assemblyclearance and thermal expansion, or deformation under high pressure. Sosuch a valve has a bidirectional seat seal under the extreme conditionsand high pressure for ANSI class 2500.(f) To provide a rotary valve with simple, low cost, reliable, highlyefficient and adaptable flow trims, so such a valve can be used forthrottling applications, it not only reduces cavitation and noise, butalso provides precision flow condition and long life and highreliability for sever service.(g) To provide a valve body with inline repairable seat feature, so aseat in the welded-end valve can be replaced without cutting out pipesor bodies and re-welding.(h) To provide a simple, compact and safe valve for easy manufacturing,operation, installation, repairing and maintenance, so the valve becomemuch greener to reduce waste, energy consumption and improve theenvironments.

Accordingly, besides objects and advantages of the present inventiondescribed in the above patent, several objects and advantages of thepresent invention are

Still further objects and advantages will become apparent from study ofthe following description and the accompanying drawings.

DRAWINGS Drawing Figures

FIG. 1 is an exploded, quarter cut view of a rotary valve constructed inaccordance with this invention.

FIG. 2 is a front view of rotary valve of FIG. 1.

FIG. 3 is a cross sectional view of rotary valve of FIG. 2 along lineA-A.

FIG. 4 is a detail views of rotary valve of FIG. 3

FIG. 5 is a cross sectional views of alternative I rings of FIG. 4.

FIG. 6 is a top view of a bearing in the rotary valve of FIG. 3.

FIG. 7 is a cross sectional view of bearing of FIG. 6. along line C-C.

FIG. 8 is a back view of rotary valve of FIG. 1.

FIG. 9 is a cross sectional view of rotary valve of FIG. 8 along lineB-B.

FIG. 10 is an iso view of a lock plug of FIG. 9

FIG. 11 is a detail view of rotary valve of FIG. 9

FIG. 12 is a detail view of rotary valve of FIG. 9

FIG. 13 is a front view of an alternative rotary valve of FIG. 1

FIG. 14 is a cross sectional view of rotary valve of FIG. 13 along lineL-L.

FIG. 15 is a detail view of rotary valve of FIG. 14

FIG. 16 is a front view of rotary valve of FIG. 1

FIG. 17 is a cross sectional view of rotary valve FIG. 16 along line G-G

FIG. 18 is a detail view of rotary valve of FIG. 16

FIG. 19 is a detail view of rotary valve of FIG. 17

FIG. 20 is an iso view of a lock plug of FIG. 19

FIG. 21 is an iso view of a lock of FIG. 19

FIG. 22 is an exploded view of an alternative rotary valve of FIG. 1

FIG. 23 is a front view of an alternative rotary valve of FIG. 21

FIG. 24 is a cross sectional view of rotary valve of FIG. 23 along lineD-D.

FIG. 25 is a an iso view of a trim of FIG. 24

FIG. 26 is a front view of an eccentric lock of FIG. 24

FIG. 27 is an iso view of a trim of FIG. 24

FIG. 28 is an exploded view of alternative valve body of FIG. 1.

FIG. 29 is a side view of valve body of FIG. 28

FIG. 30 is a cross sectional view of valve body FIG. 29 along line E-E.

FIG. 31 is a detail view of valve body of FIG. 30

Reference Number In Drawing 100 rotary valve, a, b, c, d 101 body, 102packing bore 103 flow port 105 wedge groove 106 stem hole 107 solid seat108 seat seal surface 109 seat recess 110 front surface 111 seat recessinward surface 113 seat opening 114 opening surface 115 body outsidesurface 117 position pin hole 118 step bore 119 groove 120 stem 121 Iring groove 122 keyway, 122′ 123 stem surface 124 closure memberassembly 125 I ring, 125′, 125″ 126 outside surface 127 setscrew 128packing, 128′ 129 gland 130 closure member, Disc, Ball 131 hub, 131′ 132stem hole 133 keyway, 133′ 134 step boss 135 solid seat 136 seal surface137 boss 138 back surface 139 lock slot 140 back groove 141 radialgroove 142 gap, 142′142″ 143 plug hole, 143′ 144 retreat slot 145 keyslot 146 lock plug, 146′ 147 eccentric groove 148 slot 149 thread hole150 seat ring, 150′, 150″ 151 Converting surface 153 back surface 154Inward seal surface 155 outward seal surface 156 front surface 157 key,157′ 158 wedge surface 159 tongue 160 lock ring 161 base 162 wedgesurface 163 retreat hole 164 ring 165 retaining ring 166 wedge groove167 wedge surface 168 inward surface 169 Inside diameter surface 170 Kring 171 compression ring, 171′ 172 outward surface 174 Inside surface175 bearing 176 bearing inside surface 177 slot 178 spring pin, 178′,178″ 179 position pin 180 trim, 180′ 181 port 182 outside surface 183mating surface 184 groove 185 eccentric lock 186 retreat slot 187position hole 188 flow hole 189 step 191 body ring 192 internal conicalsurface 193 cover gasket 194 bolt 196 seat cover 197 body gasket 198wedge support ring, 198′ 199 nut

DESCRIPTION

FIGS. 1-3 illustrate a rotary valve constructed in accordance with thepresent invention. The valve 100 comprises a body 101 having a packingbore 102 extended to a stem hole 106 for receiving respectively gland129, packings 128, 128′ and a K ring 170, a closure member assembly 124includes a disc 130 and a stem 120 disposed in the stem hole 106 bymeans of three spring bearings 175, disc 130 with wave seats 150, 150′is movably disposed in a port 103 for throttling flow fluid betweenclosed and open positions.

Referring FIGS. 3-7, stem 120 includes a groove 121, K ring 170 comprisetwo compression rings 171,171′ and an I ring 125 having a rectanglecross section disposed in groove 121, two compression rings 171,171′ arerespectively disposed below and above I ring 125, an inside cylindricalsurface 174 of ring 171, an inside cylindrical surface 174′ of ring 171′are tightly engaged respectively with a stem cylindrical surface 123 andan outside surface 126 of I ring 125 for providing seals as compressionrings 171, 171′ are pressed inwardly to each other, a cross section of Iring 125 can be constructed as a circle or with two wedge sides forlarge stems or as an integral part of stem 120, two laminated metalpackings 128,128′ are respectively disposed below and above K ring 170for axial and radial seals. Spring bearings 175 having a cylindricalinside surface 176 are disposed in stem hole 106 with three axial slots177 for receiving one solid and two hollow pins 178,178′, stem 120having cylindrical surface 123 is rotationally disposed in an insidesurface 176 of bearings 175, when stem 120 is rotated to a closedposition, bearing 175 with solid pin 178 is against the stem 120 anddisc 130 for eliminating cumulative clearances among stem 120, disc 130and body 101, in case of high temperature applications, at lease onespring pins 178′ will be used to compensate any thermal expansion ordeformation under load between stem 120 and bearing 175, spring pins178′ can be constructed as spiral pin or a ring with a C section.

Referring FIGS. 8, 9, 10, 11, stem 120 also comprises two wedged keyways122,122′ respectively engaged with two mating wedged sides 158,158′ ofkeys 157,157′, while disc 130 includes two hubs 131,131′ having a stemhole 132 to receive stem 120 and two keyway 133,133′ engaged with twokeys 157,157′ for transferring movements between stem 120 and disc 130,key 157′ has a flat tongue 159 inserted in a slot 139 of keyway 133′, alock plug 146′ having an eccentric groove 147′ and a drive slot 148′ ismovably disposed in plug hole 143′ of disc 130 to receive tongue 159, asplug 146′ is rotated, a bottom of groove 147′ is pressed against tongue159 for securing a joint between stem 120 and disc 130, since plug 146′is first disposed in the plug hole 143′, keys 157,157′ are inserted intokeyway 122,122′ from both side of stem 120 as stem 120 is inserted intoa middle position, groove 147′ holds tongue 159, as a result, the plug146′ and key 157′ are interlocked and will never fall out withoutdissembling the stem 120 from disc 130, while key 157 is securelydisposed between keyways 157 and 133.

Referring FIGS. 8,9, 12, two wave seats 150,150′ disposed between asolid seat 107 of body 101 and a conical boss 137 of disc 130 aredefined respectively by inward conical surfaces 154,154′, front non-flatsurfaces 156,156′, outward conical surfaces 155,155′ and back non-flatsurfaces 153,153′, front surface 156 of seat 150 is against a frontnon-flat surface 138 of disc 130 with a gap 142, a front surface 156′ ofwave seat 150′ is against back surface 153 of seat 150 with a gap 142′,a front surface 168 of a retaining ring 165 is against back surface 153′of seat 150′ with a gap 142″, as disc 130 is approached to a closeposition, conical outward seal surfaces 155,155′ are engaged with asubstantially identical angle conical surface 108 of solid seat 107 forproviding seals between wave seats 150,150′ and solid seat 107, inmeantime, wave seats 150,150′ are bended axially into gaps 142,142′142″under the radial compression, gasp 142,142′142″ become smaller, conicalinward seal surfaces 154,154′ are engaged with a substantially identicalangle conical surface 136 of boss 137 for providing seals between waveseats 150,150′ and disc 130.

Referring FIGS. 13,14,15, a rotary valve 100 a is based on valve 100,valve 100 a has a body 101 a including a recess 109 a, two wave seat 150a,150 a′ disposed between a solid seat 135 a of a disc 130 a and recess109 a are defined respectively by inward conical surfaces 154 a, 154 a′,front non-flat surfaces 156 a, 156 a′, outward conical surfaces 155 a,155 a′ and back non-flat surfaces 153 a,153 a′, front surface 156 a ofwave seat 150 a is against surface 110 a with a gap 142 a, front surface156 a′ of seat 150 a′ is against back surface 153 a of seat 150 a with agap 142 a′, a front surface 168 a of a retaining ring 165 a is againstback surface 153 a′ of seat 150 a′ with a gap 142 a″, as disc 130 a isapproached to an open position from an closed position, inwardly conicalseal surfaces 154 a,154 a′ are away from substantially identical conicalsurface 136 a of solid seat 135 a, at meantime wave seat 150 a,150 a′are tend to return to original position, while gaps 142 a, 142 a′ and142 a″ become larger and are trended to return to original shape withoutthe radial compression, while conical outward seal surfaces 155 a,155 a′are engaged with a substantially identical conical surface 111 a of boss109 a for seals.

Referring FIGS. 9,12,16,17,19, 20,21, a step cylindrical boss 134 ofdisc 130 has three substantially identical plug hole 143 respectivelywith three retreat slots 144 equally circumferentially spanned andextending to groove 140, each of three plugs 146 having an eccentricgroove 147, a drive slot 148 and a thread hole 149 is disposed in plughole 143, each of three lock rings 160 having a ring 164 with a wedgeside surface 162 and a base 161 and a retreat hole 163 is movablydisposed in groove 140, each base 161 is extend into plug hole 143 andgroove 147, retaining ring 165 having an inside cylindrical surface 169disposed on boss 134 of disc 130 has front surface 168 against wave seat150′ and a groove 166 having a wedge side surface 167, as plug 146 isrotated, a bottom of groove 147 is against base 161 outward, as aresult, lock ring 160 is moving into groove 166, wedge side surface 162of lock ring 160 is engaged with a mating wedge side surface 167 ofgroove 166 of retaining ring 165 for converting a radial movement to anaxial movement and securing seat 150′, after plug 146 is rotated fullyagainst to base 161, setscrew 127 in thread hole is tightened forpreventing plug 146 from rotation, since an angle of wedge side 162 issubstantially the same as that of wedge side surface 167 and is smallenough to have self lock effect, because lock rings 160 is inserted intogroove 166 after the plug is installed, plug 146 and lock ring 160 areinterlocked, setscrew 127 is longer than slot 148, so even plug 146 isin full loosed condition, non of plug 146 or setscrew 127 will fall out,retaining ring 165 a, lock plugs 146 a and lock rings 160 a in FIG. 15has the same function here.

Referring FIG. 22, a rotary valve 100 b based on valve 100 comprises abody 101 b, a closure assembly 124 b with a stem 120 b and a ball 130 band a wave seat 150 b secured by retaining ring 165 b and lock plugs 146b is disposed in body 101 b for controlling flow in a flow port of 103b, trims 180 b, 180 b′ are disposed in body 101 b for reducingcavitation and noise, trim 180 b with a groove 184 b is installed in aflow port 103 b and secured by two eccentric lock rings 185 b disposedin groove 119 b, while trim 180 b′ is installed in flow port 103 b andsecured by two pins 179 b and step 189 b

Referring FIGS. 23,24,25,26,27, a rotary valve 100 c based on valve 100is used for reducing cavitation and noise, valve 100 c comprises a body101 c having a flow port 103 c with a groove 119 c, two position pins179 c, two eccentric segment lock rings 185 c and a pair of trims 180c,180 c′, flow port 103 c has a groove 119 c and a step bore 118 chaving two position pin holes 117 c in an opposite direction, segmentcylindrical left trim 180 c′ is disposed in flow port 103 c byengagement between cylindrical step 189 c′ and mating step bore 118 cfor preventing trim 180 c from moving inwardly, two pins 179 c arerespectively disposed between the pin holes 117 c and position holes 187c′ of trim 180 c′ for preventing rotary movements of trim 180 c′, trims180 c′ also comprises a flow opening 181 c′ extended to spherical matingsurface 183 c′ having multiple through holes 188 c′, said closure member130 c is rotated against the mating surface 183′ for throttling a flowand reducing cavitation and noise, while segment cylindrical right trim180 c having a groove 184 c is disposed in flow port 103 c by means of apair of eccentric lock rings 185 disposed between groove 184 c andgroove 119 c for preventing trim 180 c from movement, as ring 185 c witha retreat slot 186 c is rotated, a bottom and a top of eccentric ring185 c will press bottoms of grooves 119 c 184 c for securing trim 180 c,in case of high flow rate, ring 180 c can be spot-welded with body 101c, trims 180 c also comprises a flow opening 181 c extended to aspherical mating surface 183 c having multiple through holes 188 c, saidclosure member 130 c is rotated against the mating surface 183 c forthrottling flows and reducing cavitation and noise.

Referring to FIGS. 28-31, a valve body 101 d is used for inline seatrepairable application without cutting welded pipe or valve body, valvebody 101 d based on valve body 101 comprises a conical outside surface115 d with a seat wedge opening 113 d for replacing a seat (not shown)and a mating wedge cover 196 d disposed in opening 113 d with a covergasket 197 d for providing seals, a body ring 191 d is mounted onoutside surface 115 d and secured by bolts 194 d and nuts 199 d, bodyring 191 d comprises a conical outside surface 192 d engaged with asecondary gasket 197 d and substantially identical angle conical surface115 d for providing seals and reinforcing strength of body 101 d, a pairof mating wedged seat support rings 198 d, 198 d′ is inserted into body101 d, support rings 198 d, 198 d′ are rotated for supporting andadjusting the seat horizontally.

ADVANTAGES

-   1. Reliability. (1) High operational reliability is based on the    closure member which is only one moving part secured by    wedge-eccentric lock device between the disc and stem; (a) three    spring bearings compensate any deformation of the stem under load    and absorber any impact load on the stem and reduce the stress (b)    the wedge-eccentric joint/lock device between disc and stem evenly    distributes load between middle of the disc and middle of the stem    without stress concentration and backlash reduce the hub's    overstress which happen in most butterfly valves, even the stem is    broken or under vibrations, the keys will not fall into the flow    port (c) the wedge-eccentric-thread joint/lock device between    retaining ring and seat is designed to hold the seat ring evenly and    securely, there is an interlock function between lock ring and lock    plug, the lock plugs will not fall into the flow port if the lock    ring is broken or loosen up (2) high sealing reliability is based    on (a) the wave seat seals, each metal wave seat seal has    independent outward and inward seals, seal force is self balanced    without preload, side load or side seal (b) K ring stem seal has    self energized K ring and pressure/weight balanced laminated ring    packing, the weights of stem and disc pushes the pair of compression    ring down to help seal, while internal pressure pushes the pair of    compression ring up to help seals, a pair of packing is disposed top    and button of K ring is made of laminated metal ring or laminated    graphite with metal (3) the redundancy for the seal system can be 2    to 6 as number of wave seat ring and packing increase, so it can be    used for critical applications like jet, turbine engines air    throttling or subsea flow controlling, there is no valve ever    developed which has such a high level of reliability like this valve    in this invention-   2. Sealability. The triple offset mechanism only reduces or    eliminates the rubbing between seat and closure member between    closed and open positions, whether or not it can seal at closed    position is other matter. For the first time in the metal butterfly    valve history, the wave seat finally resolve the foundational issue    for the metal seal butterfly valve, this valve is fully metal-sealed    in both static and dynamic manners with ANSI Class VI leakage or    bubble tight seal between ANSI class 150-4500, there is no    temperature barrier or limit by seal materials like graphite, the    seal capacity can take on working temperature between −250 F to 1450    F and to more with highly oxidative fluid or fluid with solid    particles, while stem leakage can be between 3-50 ppm with seat    sealing surface of fine surface 16 RMS or special coatings gold,    sliver and nickel, since the seal assembly in the valve is self    energized, compensated and pressure assistant seal, the all seal    materials can be the same, there is no constant local adjustment for    the whole valve.-   3. Durability. It is related to four wearing compensation factors    between the two parts (1) the novel metal spring bearings compensate    any wearing between stem and bearing and absorber impact force due    to opening and closing and prolongs life of stem (2) K ring with    laminated metal packing provides a forever seal mechanism, any    wearing between K ring and packings is compensated by self energized    compression ring, downward force caused by weights of stem and disc    and upward force caused by internal pressure (3) the wave seat seal    acts as a disc spring to store torsion energy when it is approached    to closed position and release torsion energy when it is approached    to open position, as result the wearing and tearing due to the    friction can be further reduced, the operating torque is only 50 to    65% of conventional metal butterfly operating torque, moreover the    wave seat acts as a self balanced spring to compensate any wearing    on the inward surface or outward surface within a limitedly known    range of torque, while conventional metal seal butterfly valves act    as an energy dissipater both in closing and opening processes, so    the torsion energy can not be destroy or created, so the energy    become heat and damages the seat in both closing and opening by    forms of friction and heat, in meanwhile, all seals and spring    bearing are self energized to compensate any wearing (4) non    backlash key joint between the stem and disc eliminates any wearing    between them, further the join comes with interlock and falling    proof mechanisms, with all benefits of the invention, the valve can    last 5 to 30 years without replacement or readjustment and away    beyond any existing valve life in the valve industries-   4. Efficiency. High efficiency comes from two aspects; operation and    maintenance (1) with a pair of left and right replaceable trims for    reducing noise and cavitations in between 0-60 degrees where most    likely noise and cavitations happen, the capacity of this valve with    the trims only reduce by 20% in comparison with 50 to 60% of    capacity reduction for the same size control valve with noise and    cavitation full trims, the trims can be easily replaced and    installed between flange ends with pins or with eccentric lock rings    and with triple offset ball, the valve can handle full port or    reduced port applications (2) the inline repairable body is other    advantage to keep cost down, the opening cover is cut from the    original body, only things need are the gaskets and taped cover    ring, wave seat rings can be easily replaced with seat wedge    adjustable ring to secure the seats, yet the body is robust looks    beautiful unlike conventional inline repairable body, in short, this    invention enable the butterfly valve to break the ANSI class 1500    and 2500 barrier as good options to replace the high pressure ball    and gate valve with compact and robust body with the weights about    40% of the same size ball valve weights or 70% of the same size gate    valve.

CONCLUSION, RAMIFICATIONS AND SCOPE

The present invention provides a revolutionary solution for fully metalto metal seal rotary valves, the wave seat in this invention finallysolve the metal to metal seal problem, it complete change theconventional rotary metal seal, there are three distinguish differencesbetween the conventional laminated seat and the wave seat (a) the waveseat completely eliminate graphite and the glue, so it breaks thetemperature limit beyond 850 F for both dynamic and static seals,specially in jet or rocket engine applications where it is used forthrottling high temperature, highly oxidative flows (b) each wave seathas a balanced, independent inward and outward seals and act as areverse disc spring, it store and release torsion energy unlike theconventional triple offset butterfly valve as an energy dissipater, itnot only reduces the torque by 40% and wearing, but increase life of thewave seat, while the conventional laminated seat has metal rings gluedwith graphite rings together and only one layer first or last to preventleak in inward or outward seal seals, if the seal layer leaks, the wholeseat will leak, while each wave seat has independent seals, based onlocation, front and back seat can be harder to handle fluid with theparticle and buildup and provide good dynamic seals, while middle waveseat can be flexible to good static seals, so it be used for boththrottling and shutoff (c) the wave seat has non-flat front and backsurfaces without pre-side load and side seals, so any open or closedoperation will not generate much friction or heat between the waveseats, such feature greatly increase the sealability as well as thelife, the three features are co-existing, without one, the other twocannot exist, with the features the metal seal rotary valve finally cancompete against conventional ball valve as well as gate valve at highpressure/temperature applications and sever service, while both gate andball valve still struggled with unsolvable rubbing problem and toughmetal seal issues for special applications where constant replacement ofseat is impracticable like subsea devices, nuclear power plants.Finally, wave seats can installed on both the disc and body at the sametime, so the replacement will be much cheap and easy in high erosiveflow applications or under most sever conditions, while it is requiredthat the ANSI class VI leakage, the body and disc will not replaced butthe wave seat does, even wave seats to be replaced can last 5 to 30years, the wave seat can maintain the class VI seal without replacement,second is outward and inward balanced surface seals, such a seal has noany back seat leak, when wave seat at open position is not undercompression, there is no seal need, when wave seat at closed position,the seal force is balanced by inward and outward surfaces, while theseal force in the conventional metal seal butterfly is weakening thegraphite side seal and preload to maintain the seal and unbalancedconstantly

The present invention provides a long sought solution—a novelwedge-eccentric—thread joint/lock mechanism to two fundamental problems;one is bolting joint between seat and retaining ring, other is key/pinjoint between stem and disc in the conventional valve

(a) This wedge-eccentric-thread joint/lock mechanism completely changethe way of joint/lock between seat and retaining ring (1) 3 or 4 of lockrings to replace 4 to 36 of bolts for securing the retaining ring in thetriple offset valve, the locking rings not only reduce the machiningtime and parts, risk of number of un-tighten bolts, but increase contactarea about 3 to 4 times and the reliability of the joint by evenlydistributing compression force on the retaining ring (2) theirreversible, redundant, independent wedge-eccentric join/lock mechanismto replace reversible, multiple, non-independent bolting join/lockmechanism, each wedge-eccentric join/lock mechanism is operated by achain of function of setscrew for preventing rotation of lock plugs, thefriction amplified by special surface textures or coatings between thelock plug hole and lock plug for preventing rotation of lock plugs, thewedge engagement with self lock angle between lock ring and groove ofthe retaining ring for preventing radial inward movement of lock ring,three or four wedge-eccentric-thread joint/lock mechanisms provide threeor four redundancies of joint/locking, so any failure of one of thewedge-eccentric-thread join/lock mechanisms will not effect the othermechanisms, any failure of each wedge-eccentric-thread joint/lockmechanisms against the seat has to be accomplished by a series ofactions of loosing setscrew, rotation of lock plug, inwardly radialmovement of lock ring at the same time, but such a possibility is nextto zero, with such high reliability, the valve can be used even undermultiple extreme conditions such as a high vibration and hightemperature like turbine engine applications due to different naturesbetween wedge and eccentric mechanisms (b) This wedge-eccentric-threadjoint/lock mechanism provides other solution for joint between stem anddisc, with the middle balance keyways on the disc and two wedges on thestem, the wedge key joint evenly distributes the loading between hubs ascompression, because of the wedge engagement between stem and keys, thestem no longer has high stress concentration, the clearance between stemand keys become one dimension unlike conventional keyway with twoclearance in X and Y dimensions, the lock plug engaged with the wedgekey on one side or two side can eliminated the clearance between stemand keys to prevent loss motion and backlash, which is very importantfor automation control, in term manufacturing process, cross milling thewedges on the stem is much easier and lower cost than the broaching orposition milling keyway on the stem, moreover, wedged key will not fallin a pipeline system even under a loose condition, the load underpressure is shifted from the disc hubs and stem hub joint in theconventional butterfly valve to the center strong section of the discand the stem, with the self lock angles, friction amplified texturesurfaces and anti-loose screws, no screws will not loosen because ofvibration or reaction forces, moreover, all bases are constantly engagedwith grooves, length of setscrew is longer than that of slot, so no lockplug or setscrew will fall out, more importantly thewedge-eccentric-thread mechanism can be used for any other valves suchas plug valves, ball valve, control valve and gate valves.

The invention provides a breakthrough stem seal concept, just anopposite way to wave seat seal, it converts a dynamic radial seal to andynamic axial seal, K ring 170 converts a radial seal on stem 120 to anaxial seal between compression rings 171,171′ and packings 128,128′,according to hook law and Poisson ratio, preload on an axial seal isabout ¼ of a radial seal, the conventional large gland, large bolts andexceed load are no longer needed in an axial seal, it is fire safe bynature, compression rings 171,171′ are metal, I ring 125 can become ofpart of the stem or made out of any material, metal, graphite, PTFE, inaddition, since compression rings 171,171′ are fixed with stem 120 undercompression, it acts a soft stem holder and reduce wearing on seats150,150′.

Other problem the invention solves is bidirectional seal, many valvemakes claim that their triple offset valves are bidirectional, in factwhen the valve is used for upstream seal, most valves will leak due tonature of the design and cumulative clearances, but with spring bearings175 in this invention, when valve 100 is used for upstream seal, thespring bearing 175 with three pins is installed in stem hole, one solidpin is disposed in flow port direction, there are two spring pinsinstalled in two opposite directional slots, so stem 120 is at an openposition, stem 120 is rotated freely in the bearings, when stem 120 isclosed position, all clearances are pressed against solid pin direction,while spring bearings with at least one spring pin can be used for hightemperature applications, it will compensate thermal expansion ofbearing 175 as well as stem 120.

The left and right trims in this invention provides a simple, low cost,flexible and effective solution for noise/cavitation reducing, itcomprises a segment cylindrical bar having multiple holes, internalmating surface and flow port, the novel flexible connecting methods andthe compact half cylindrical structure provide a wide applications,either with step bore and two position pins for flange, lug and waferstyle bodies or eccentric lock ring disposed in two grooves on body andtrim for long pattern bodies, they can be used either for retrofit withadditional flanges, where sever cavitation happens or complete newvalves, the trims not only save lot of material in comparison withconventional trims either complete cylindrical trim or a disc with anintegral part of trims, but also provide more flow restriction wherecavitation happens, more flow space where restricting flow isunnecessary, the multiple flow holes with internal mating surfaceprovides a very effective way of dissipating the flow energy betweenfluid—solid interaction and reduce the velocity and noise.

Finally the inline seat repairable body is other novel feature, it cansave million dollars for fully welded valve either butterfly valve orball valve, in most situations, only the seat is damaged, the seat costis a small percentage of total cost of valve, but whole valve must bereplaced, but with this feature, million valves will be saved, it isconstructed as standard valve body with additional cutting, openingcover from original body will be reused along with gasket, body ringwith a secondary gasket is provided for sealing and reinforcement, acomparison test indicates wedge opening structure is stronger than theconventional flat top openings by 15 to 30% and less leakage.

Although the description above contains many specifications, theseshould not be construed as limiting the scope of the invention but asmerely providing illustration of some of the presently preferredembodiments of this invention.

Thus, the scope of the invention should be determined by the appendedclaims and their legal equivalents, rather than by the examples given.

1. A fluid related device comprising; (a) A body assembly having a bodyincluding at least one flow port; (b) At least one closure memberassembly including a stem and a closure member movably positioned insaid flow port; (c) At least one seal assembly means for providing sealsbetween said body and said closure member assembly.
 2. The device ofclaim 1, wherein said seal assembly disposed between said flow port andsaid closure member including at least one seat defined by an inwardconical seal surface, an outward conical seal surface and a non-sealfront surface having a plurality of profiles including a non-flatsurface, a flat surface and wave surface and a non-seal back surfaceincluding a plurality of profiles including a non-flat surface, a flatsurface and wave surface.
 3. The device of claim 2, wherein said flowport including a mating conical sealing surface engaged with saidoutward surface of said seat for providing seals at a closed position ofsaid closure member, said closure member having a boss defined by amating conical surface engaged with said inward surface of said seat forproviding seals.
 4. The device of claim 2, wherein said flow portincluding a recess defined by a mating conical surface engaged with saidoutward surface of said seat for providing seals, said closure memberhaving a mating conical outward surface engaged with said inward surfaceof said seat for providing seals at a closed position of said closuremember.
 5. The device of claim 2, said flow port including a recessdefined by a mating conical surface engaged with said outward surface offirst said seat for seals, said closure member having a boss defined bya mating conical surface engaged with said inward surface of second saidseat for seals, said mating inward surface of first said seat engagedwith said outward surface of second said seat for seals at a closedposition.
 6. The device of claim 2, said seat constructed with aplurality of base materials including AISI-0175, Alloy 6150, Inconel 750and 718, stainless steel 17-7, PTFE, PEEK, polymeric materials and witha plurality of surface coating materials including gold, sliver, nickel,chrome and PTFE.
 7. The device of claim 1, wherein said closure memberassembly including at least one joint/lock means comprising; (a) A wedgemeans including at lease one active wedge part defined by a wedgesurface and one passive wedge part defined by a mating wedge surfaceengaged with said wedge surface of said active wedge part for convertingmovements, said wedge means having a plurality of forms including (1)said active wedge part constructed as a lock ring defined by a conicalwedge surface, said passive wedge part constructed as a retaining ringdisposed in a mating cylindrical boss of said closure member having agroove defined by a mating conical wedge surface engaged with saidconical wedge surface of said lock ring (2) said active wedge partconstructed as a key disposed in a keyway of middle of said disc definedby a flat wedge surface, said passive wedge part constructed as a stemdisposed in a stem hole between two hubs of said disc having a keywaydefined by a mating flat wedge surface engaged with said flat wedgesurface of said key; (b) An eccentric means for converting rotarymovements to linear movements including an active rotary part defined byat least one centric cylindrical surface, at least one eccentric annularopening having a plurality of cross sectional shapes including circle,polygon, oval and multiple curves, a combination of lines and curves anda converting part of said active wedge part engaged with said eccentricannular opening, said eccentric means having a plurality of formsincluding; (1) said active rotary part constructed as a centriccylindrical lock plug disposed in a hole of said disc having aneccentric cylindrical groove, said converting part of said active wedgepart constructed as a base of said lock ring engaged with said eccentriccylindrical groove of said plug (2) said active rotary part constructedas a centric cylindrical lock plug disposed in a hole extending to aslot of said keyway of said disc having a groove defined by an eccentriccylindrical surface, said converting part of said active wedge partconstructed as said key disposed in said keyway having a tongue engagedwith said eccentric cylindrical groove of said plug and said slot. 8.The device of claim 7, wherein said joint/lock means including a lockingmeans having a screw and said lock plug including a driving slot on atop of said plug for operation and a screw slot extending vertically tothread hole to receive said screw for preventing said plug fromrotation, said screw having a longer length than a length of said screwslot for preventing screw from failing out.
 9. The device of claim 7,wherein said base of said lock ring also including a retreat hole, saiddisc having at lease one retreat slot for an access of said retreat holewhen said lock ring at an upper position.
 10. The device of claim 1,wherein said body assembly including at least one joint/lock meanscomprising; (1) A wedge means including at lease one active wedge partdefined by a wedge surface and one passive wedge part defined by amating wedge surface engaged with said wedge surface of said activewedge part for converting movements, said wedge means having a pluralityof forms including; said active wedge part constructed as a lock ringdefined by a conical wedge surface, said passive wedge part constructedas a retaining ring disposed in a mating cylindrical recess of said bodyhaving a groove defined by a mating conical wedge surface engaged withsaid conical wedge surface of said lock ring (2) An eccentric means forconverting rotary movements to linear movements including an activerotary part defined by at least one centric cylindrical surface, oneeccentric annular opening having a plurality of cross sectional shapesincluding circle, polygon, oval and multiple curves, a combination oflines and curves and a converting part of said active wedge part engagedwith said eccentric annular opening, said eccentric means having aplurality of forms including; said active rotary part constructed as acentric cylindrical lock plug disposed in a hole of said body having agroove defined by an eccentric cylindrical surface, said lock ringhaving a base constructed as said converting part of said active wedgepart engaged with said eccentric groove of said plug.
 11. The device ofclaim 10, wherein said joint/lock means including a locking meansincluding a screw and said lock plug including a driving slot on a topof said plug for operation and a screw slot extending vertically tothread hole to receive said screw for preventing said plug fromrotation, said screw having a longer length than a length of said screwslot for preventing screw from failing out.
 12. The device of claim 10,wherein said base of said lock ring also including a retreat hole, saidbody having at lease one retreat slot for an access of said retreat holewhen said lock ring at an upper position.
 13. The device of claim 1,wherein said seal assembly including a stem seal, said stem seal havingan I ring and a pair of compression rings with a cross section of Vshape, said stem having a cylindrical surface including a groove toreceive said I ring, said I ring including a plurality of crosssectional shapes including circle and a polygon having two sidesrespectively engaged with a side of each said compression ring, said Iring including a plurality of construction methods including as anintegral part of said stem and a separated part, said compress ringhaving a static sealing surface engaged with said I ring for seals andan outward dynamic seal surface, said outward dynamic seal surfaceincluding a plurality of profiles including a conical surface andspherical surface.
 14. The device of claim 13, wherein said sealassembly including a pair packings respectively engaged with said twodynamic outward sealing surfaces of said compression rings for providingseals among said stem seal and said packings, said packing constructedwith a plurality of materials including laminated metal rings, laminatedmetal and graphite rings, laminated graphite rings and laminatedpolymeric rings.
 15. The device of claim 1, wherein said body assemblyincluding at least one bearing disposed between said body and said stem,said bearing having at lease two vertical slots and at least two springpins movably respectively disposed into said slots, said pin including aplurality of cross sectional shapes including a circular shape, circularring shape, spiral shape and C shape.
 16. The device of claim 1, whereinsaid body assembly including a pair of trims respectively disposed inboth ends of said flow port, a left trim of said pair of trims having aleft segment cylindrical ring including a flow opening extended to aspherical mating surface having multiple through holes against saidclosure member for throttling flows and reducing cavitations and noise,a right trim of said pair of trims having a right segment cylindricalring including a flow opening extended to spherical mating surfacehaving multiple through holes against said closure member for throttlingflows and reducing cavitations and noise.
 17. The device of claim 16,wherein said body assembly including at least two lock means, a firstlock means of said two lock means for securing said trim on said bodyincluding a step bore on said body and two pin holes on said step borein an opposite direction, said trim also including a segment step matingring having two cylindrical mating slots in said ring disposed in saidstep bore of said body by means of said two pins respectively disposedbetween said two pin holes on said body and said two cylindrical matingslots on said ring for preventing rotation of said trim and engagementbetween said step bore and said step mating ring for preventing inwardlinear movements of said trim, a second lock means of said two lockmeans for securing said trims on said body including a groove betweensaid flow port and said trim, a pair of eccentric lock rings disposed insaid groove for preventing said trim from movements, each of saideccentric lock rings disposed in said groove with a clearance fitdefined by an outside cylindrical surface based on one center and aninside cylindrical surface based on other center with a slot.
 18. Thedevice of claim 1, wherein said body assembly including a seatrepairable body having a wedge opening, a wedge cover disposed in saidopening and a cover gasket disposed between said opening and said coverfor providing seals, said body also having conical outside surface andat least four thread holes, said body assembly also including a bodyring having at least four bolts and a mating conical surface engagedwith said conical surface of said body and a body gasket for secondaryseal and secured by said bolts between said thread holes on said bodyand said body ring, said body assembly also including a pair of wedgesupport rings disposed in said body for supporting said seat by rotatingone of said rings.
 19. The device of claim 1, wherein said bodyincluding a plurality of styles including a flanged style, a welded endstyle, a wafer style, a lug style, a threaded end style and a seatrepairable style.